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964 0.1:. ROSAEN E 3,117,528

VARIABLE DELIVERY VANE PUMP Filed April 22. 1959 4 Sheets-Sheet 1 .INVENTOR. OSCAR E ROSAEN ATTORNEYS Jan. 14, 1964 o ROSAEN 3,117,528

VARIABLE DELIVERY VANE PUMP Filed April 22, 1959 4 Sheets-Sheet 2 g has I mmvrox 38 OSCAREROSAEN ATTO RN EYS 13111.14, 1964 0.1:. RO AEN 3,117,528

VARIABLE DELIVERY JANE PUMP Filed April 22, 1959 4 Sheets-Sheet :5 2

I 5 I 'O Bin INVENTOR. OSCAR a ROSAEN ATTORNEYS Jan. 14, 1964 o. E. ROSAEN 3,1 17,528 VARIABLE DELIVERY VANE PUMP Filed April 22, 1959 4 Sheets-Sheet 4 INVENTOR.

I OSCAR E. ROSAEN ATTORNEYS United States Patent G 3,117,528 VARIABLE DELIVERY VANE PUMP Oscar E. Resaen, 51 Roslyn Read, Grosse Pointe Fmms, Mich. Filed Apr. 22, 1959, Ser. No. 868,168 Illaims. (1. 193-135) The present invention relates to rotary vane type pumps and more specifically to variable delivery vane type pumps.

Among the objects of the invention is to provide a pump which may be adjusted to deliver fluid at a given pressure and will then automatically vary its delivery to maintain such pressure.

Another object of the invention is to provide a pump in which the eccentricity of the rotor within the pump chamber is automatically varied to vary the fluid delivery.

Another object is to provide means to prevent overheating of the pump.

Still another object is to provide a novel type of rotor and vanes therefor.

Other objects and advantages will readily occur to those skilled in the art upon reference to the following description and the accompanying drawings in which:

FIGURE 1 is a plan view of the pump as if taken from the top of FIGS. 2 and 3.

FIGURE 2 is a sectional view taken on the line 2-2 of FIG. 3.

FIGURE 3 is a sectional view taken on the line 3-3 of FIG. 2.

FIGURE 4 is an enlargement of a portion of FIG. 3.

FIGURE 5 is a partial view in elevation of the inner face of the check plate 17, Le. the left hand cheek plate as seen in FIG. 2.

FIGURE 6 is a partial edge view of the same.

FIGURES 7 and 8 are respectively a plan and edge view of a detail of construction.

FIGURE 9 is a plan view of the rotor and cam ring of a constant delivery pump using similar vanes.

FIGURE 10 is a view similar to FIG. 9 but showing the locations of the inlets, outlets, etc.

In FIG. 1 of the drawings the pump is shown in elevation and indicated as having a body portion A, provided with a mounting flange or base B, a main fluid inlet at C, and a secondary inlet at D. One end of a drive shaft is shown at E, the other end being hidden by the superstructure F.

The body A is closed by an end plate 10 (FIG. 2) through which one end of the shaft E extends being provided with a suitable antifriction bearing such as the roller bearing 11 and a suitable oil ring 12. The other end of the shaft E is similarly mounted in the closed end of the body A as indicated at 11A and 12A.

Intermediate the ends of shaft E is mounted a rotor 15, which may be integral with the shaft or otherwise fixed thereto, and enclosing the rotor is a pump casing consisting of the cheek plates 16 and 17 arranged at the side faces of the rotor, and the cam or pump ring 18 surrounding but spaced from the rotor. The plates 16 and 17 and ring 18 are fixed together as a unit by means of suitable screws. The ring 18 is of such width as to provide a suitable sliding fit for the rotor between the cheek plates.

The openings in the cheek plates 16 and 17 for the passage of the shaft end portions are somewhat larger than the shaft, so that the pump enclosing unit is movable radially relative to the shaft and rotor.

The rotor enclosing unit of cheek plates and ring is supported in the outside casing by means of two pins 20 and 21 which are provided with spherical ends and seated in suitable sockets in opposite portions of ring 18 and in pistons 20A and 21A respectively carried in the lower ice and upper walls of the outer casing, the pistons being also provided with suitable sockets for the spherical ends of the pins.

Also carried in the ring 18 is an outlet element 22 provided with passages 23 and spherical outer end 22A coacting with a suitable socket in the outlet casing and serving as conduit means leading the fluid from the chamber 19 into the outlet 24. Chamber 19 is an arcuate recess in the ring 18 open to the inner periphery thereof.

As shown in FIGS. 3 and 4, the rotor 15 consists of a disc of substantial thickness having in its periphery a plurality of curved slots 25, at the inner ends of which are enlarged through passages 26 and in each slot is slidably carried a curved vane 27, the outer end of which is arcuate and with the radius as that of the inner periphery of ring 18. In FIG. 4, the enclosing circle 18A represents the inner surface of ring 18.

The two cheek plates 16 and 17 are cut away for a portion of their peripheries at the edge opposite the outlet 24, the cutaway portion being indicated by the dotted lines 30 and full line 30A in FIG. 3 and full lines in FIG. 5. V

Cheek plate 16 in its inner face is provided with a recess in which is carried a smaller annular plate 160, shown in detail in FIGS. 7 and 8, by means of which axial pressure is exerted upon the rotor 15 to force the latter against the other cheek plate 17.

As shown in FIG. 8, plate 160 has one edge beveled as at 161 for somewhat over half its periphery and in the same face is provided with a groove 162 extending from one end of the bevel inwardly to adjacent the central opening, around this and to the other end of the bevel. In this groove 162 will be mounted a suitable gasket. Communicating with the bevel 161 is a notch 163 in the outer edge of the plate. The diameter of plate 160 is the same as that of the inner surface of ring 18 and by means of a locating piece 164 the plate 160 is so oriented that the notch 163 is exposed to fluid pressure in the pump chamber.

Cheek plate 17 is shown by itself in FIGS. '5 and 6 which show the inner face. As shown in FIG. 5, the plate is provided with an arcuate slot in position to register with the passages 26 in the rotor, which slot is in registry during pump delivery. The plate 17 also is provided with a second arcuate slot 36 which registers with the passages 26 during intake. Slot 36 communicates with the outside of the pump unit through axially extending passage 37 and a cutaway sector 38 open to the housing.

Plate 17 is also provided with a radial passage 40, plugged at its outer end and having at its inner end a valve seat for the spring pressed ball valve 41. Passage 40 opens at its inner end 42 to the slot 35 and is provided with an outlet 43 which opens to the pumping space outside of the rotor.

Plate 17 is also provided with a passage 45 extending from a location in which its inlet 46 is in position to register with the rotor passages 26 to a point somewhat ahead of the inlet and has its outlet 47 open to the pump space outside of the rotor.

As stated above, the pump unit is positioned within the housing by the pins 20 and 21 which in turn are seated in pistons 20A and 21A respectively.

As shown in FIG. 3, pin 2t) and piston 20A are bored alongitudinally to provide a passage 2013 leading to the chamber under the piston and in the chamber is also located a spring 20C tending to move the piston upwardly. The upper end of passage 26B opens to a passage 26]) leading from the pump chamber.

The pin 21 is seated in a piston 21A, the upper end of which is inclined or cammed as indicated at to coact with an inclined surface or cam on a plunger 61 arranged horizontally within the superstructure F. Plunger 61 is adjustably spring pressed toward the left (FIG. 2) by spring 62, the tension being regulated by means of screw 63.

Opposing spring 62 is a piston 63 operating in a small cylinder 64 in the closure 65 for the end of the structure F, and opening into the cylinder 64 is a conduit 66 (FIG. 1) leading to the outlet 24- of the pump. Leading from cylinder 64 is a small conduit 70 connected with conduit '71 which in turn opens to a nozzle or jet '72, the jet opening 73 of which is directed into the auxiliary supply conduit D in an outward direction.

The opening to conduit 70 is so located with respect to cylinder 64 and piston 63, that it is opened only when a predetermined pressure in the pump outlet has moved the piston and thereby plunger 61 toward the right (FIG. 2) and, in so doing, has moved the pump unit downwardly and thereby changed the relative position of the rotor and cam ring. When the rotor has been moved to a substantially concentric position, little or no pumping takes place, but, as the parts are in motion, heating will take place unless prevented. In the usual pumping action, heating is overcome by having the pump unit enveloped in the oil in the outer casing or body A. This oil is being constantly replaced by inflowing cool oil. However, if the delivery pressure builds up to the point where the delivery substantially stops due to the concentricity of the rotor, inflow of cool oil would stop. In the present pump, however, the oil from jet 73 causes outflow of oil from the casing and consequent replacement by cool oil. Of course, when the pump is delivering in large volume, both C and D act as inlets.

In the operation of the present pump, oil from the outer casing flows into the pump chamber through the arcuate cutaway 39 of the cheek plates into the intravane spaces and into the portions 26 of the vane slots.

Looking at FIG. 4, it will be seen that the intra-vanc spaces, for example, 1%1i)1192, enlarge as the rotor moves counterclockwise, 181 being larger than 1th etc., until a vane slot leaves the recess 36. With the vase moving outward and the slot being cut off from further inflow from recess 36, means is provided to maintain the pressure in the slot. This means is the passage 45 which allows flow from the pump chamber ahead of the vane down to the slot as illustrated by the dotted line vane and slot in FIG. 4-. Immediately after the opening 46 is closed to the slot, the latter opens to the arcuate slot 35 and remains so until the vane has been forced completely inward by the cam ring.

As the vanes are moved radially inward by the cam ring, the pressure developed in the arcuate slot 35 may become excessive. Means is therefore provided to control such pressure. This control means is shown in FIG. 5 as the passage 459 into which fluid from the arcuate passage 35 is admitted past the spring tensioned valve .41, which fluid then flows from the opening 43 into the outlet.

In pumps of the vane type, one of the difliculties is the excessive wear on the cam ring and the outer ends of the vanes due to the considerable pressure of the vanes against the ring. In the present pump, the form of vane shown provides automatically means for balancing the outward pressure by exposing a greater portion of the outer end area of the vane to the pumping pressure.

FIG. 4 shows clearly that as a vane moves across the horizontal center at the right of the figure, the forward edge area is being lifted from contact with the ring, and this condition obtains until the vane reaches the line at the left of the figure. At about this position, substantially the full end area of the vane contacts the ring but immediately the rearward edge area begins to lift out of contact.

As a result of this movement, fluid under the higher pumping pressures may flow into the space thus provided at all times,.except at the instant that the full end area is i in contact, and when the rotor is eccentric, this instant does not occur. The balancing action is therefore always in operation.

As indicated in the drawings, the curved vanes may also be used in vane pumps of the constant delivery type. The cam ring and rotor of such a pump is shown in FIGS. 9 and 10. The ring is indicated at 118 and the rotor disc at provided in its periphery with slots in which are slidable the vanes 127. The cam ring in this form of pump will have diametrically opposite pumping zones P with idle zones R between. The radius of the zones R is only slightly greater than the radius of the rotor 115. The radius of the pumping zones P is however considerably greater than that of the rotor, allowing the vanes to slide out of the slots a substantial distance. Using the curved vanes, the radius of the pump zones may be increased over that allowable when straight vanes are used so that for a given size, the pumping capacity may be somewhat increased. A much greater increase in capacity may be had, however, by increasing the axial dimension of the rotor, the curved vanes not being subject to cooking; that is, becoming out of parallel with the rotor axis.

In producing the rotors for either form of pump, the radius of the curve of the slot should be somewhat less than the distance between the slotssay about three quarters of the distance. While, the radius length is not critical, a too long or too short radius willprovide a slot that is less effective. In the drawing, the centers of the slot curves are ahead of the slots as indicated at C, and while the point C is shown as the perimeter of the rotor disc 115, it may be radially inward or outward of such location.

The vanes in FIGS. 9 and 10 have of course the same curvature as the slots and their outer ends will be ground as on the line G which is an arc of a circle having a radius which is the mean between the two radii of the inner surface of the ring 118.

With the outer ends of the vanes thus shaped, that edge of the vane which is the edge ofthe face under pressure, will always be slightly spaced from the cam ring and allow the fluid pressure in the pump chamber to balance pressure in the slot 126 tending to thrust the vane outwardly.

The present application is in part a continuation of my copending application Serial No. 742,095, filed June 16, 1958, for Variable Delivery Vane Type Fluid Pump, now abandoned.

I claim:

1. In a vane type fluid pump comprising a rotor provided with vane slots arranged in a substantially radial direction in its periphery, and with vanes slidable in said slots, and a pump ring surrounding the rotor and controlling the sliding of said vanes, means for admitting fluid to the spaces between said vanes, means for admitting fluid at inlet pressure to the slots under said vanes, said admissions being during that portion of the rotor rotation in which the vanes are moving outward of said slots, means for maintaining at low pressure as compared to delivery pressure the fluid in the vane slots during that portion of the rotation in which the vanes are at substantially their outermost positions and means for resiliently resisting and controlling the outflow of fluid fromthe slots under said vanes during that portion of the rotation in which the vanes are being moved by the ring inwardly of the slots.

2. In a vane type fluid pump comprising a rotor provided with vane slots arranged in a substantially radial direction in its periphery and with vanes slidable in said slots, and a pump ring surrounding the rotor and controlling the sliding of said vanes, means for admitting fluid to the spaces between said vanes, means for admitting fluid at inlet pressure to the slots under said vanes, said admissions being during that portion of the rotor rotation in which the vanes are moving outward of said slots,

means for maintaining at low pressure as compared to delivery pressure the fluid in the vane slots during that portion of the rotation in which the vanes are at substantially their outermost position, said low pressure being determined by the difierence between the outward and the inward thrusts exerted by the fluid on the outer and inner ends of the vanes.

3. In a fluid pump of the vane type, a rotor provided in its periphery with a plurality of equally spaced slots all extending in a generally radial direction of said rotor and formed arcuate about centers located at the periphery of the rotor and adjacent the next slot forward in the direction of rotation, and similarly curved vanes carried in said slots and slidable in a radial direction.

4. In a fiuid pump of the vane type, a rotor provided in its periphery with a plurality of equally spaced slots all extending in a generally radial direction of said rotor and formed arcuate about centers located at the periphery of the rotor and adjacent the next slot forward in the direction of rotation, and similarly curved vanes carried in said slots and slidable in a radial direction, a cam ring surrounding said rotor and forming pumping and idle zones therewith and contacting said vanes and determining the outward movement thereof, said vanes having the surfaces contacting said ring arcuate with a radius which is the mean of the inside surfaces of said ring in said pumping and idle zones.

5. In a fluid pump of the vane type, a rotor provided in its periphery with a plurality of equally spaced slots all extending in a generally radial direction of said rotor 6 and formed arcuate about centers located at substantially the periphery of the rotor and approximately three quarters of the distance between adjacent slots ahead of the slot with respect to the direction of rotation, and similarly curved vanes carried in said slots and slidable in a radial direction.

References Cited in the file of this patent UNITED STATES PATENTS 275,667 Jones Apr. 10, 1883 410,747 Young Sept. 10, 1889 471,279 Taber Mar. 22, 1892 630,013 Taber Aug. 1, 1899 993,648 Calkins May 30, 1911 1,123,977 Baker et al Jan. 5, 1915 1,805,063 Wrona May 12, 1931 1,820,009 Blackmer Aug. 25, 1931 2,141,171 Centervall Dec. 27, 1938 2,255,781 Kendrick Sept. 16, 1941 2,272,635 Davis Feb. 10, 1942 2,492,868 Johnson Dec. 27, 1949 2,555,679 Cornwell June 5, 1951 2,805,628 Herndon et a1. Sept. 10, 1957 2,872,873 Gardiner Feb. 10, 1959 2,878,755 OConnor et a1 Mar. 24, 1959 2,884,865 Pettibone May 5, 1959 2,962,972 Van Meter Dec. 6, 1960 FOREIGN PATENTS 580,098 Great Britain Aug. 27, 1946 

1. IN A VANE TYPE FLUID PUMP COMPRISING A ROTOR PROVIDED WITH VANE SLOTS ARRANGED IN A SUBSTANTIALLY RADIAL DIRECTION IN ITS PERIPHERY, AND WITH VANES SLIDABLE IN SAID SLOTS, AND A PUMP RING SURROUNDING THE ROTOR AND CONTROLLING THE SLIDING OF SAID VANES, MEANS FOR ADMITTING FLUID TO THE SPACES BETWEEN SAID VANES, MEANS FOR ADMITTING FLUID AT INLET PRESSURE TO THE SLOTS UNDER SAID VANES, SAID ADMISSIONS BEING DURING THAT PORTION OF THE ROTOR ROTATION IN WHICH THE VANES ARE MOVING OUTWARD OF SAID SLOTS, MEANS FOR MAINTAINING AT LOW PRESSURE AS COMPARED TO DELIVERY PRESSURE THE FLUID IN THE VANE SLOTS DURING THAT PORTION OF THE ROTATION IN WHICH THE VANES ARE AT SUBSTANTIALLY THEIR OUTERMOST POSITIONS AND MEANS FOR RESILIENTLY RESISTING AND CONTROLLING THE OUTFLOW OF FLUID FROM THE SLOTS UNDER SAID VANES DURING THAT PORTION OF THE ROTATION IN WHICH THE VANES ARE BEING MOVED BY THE RING INWARDLY OF THE SLOTS. 